Conditioning roll mounting structure

ABSTRACT

A conditioning roll mounting structure is disclosed wherein the mounting shaft for the conditioning roll is permitted to be rotatably driven while permitted to reciprocate linearly transversely of the bearing apparatus. A bushing in the form of a support hub having an antifriction surface engaged with a non-circular conditioning roll mounting shaft is pressed within the inner race of a ball bearing whose outer race is secured to the frame of the hay harvesting machine. A drive mechanism can be attached to either the support hub or directly to the shaft provided that provisions are made for accommodating the transversely reciprocating roll movement. The structure permits the conditioning roll to be rotatably supported within the frame of the hay harvesting machine, while being capable of a linear movement between the non-circular conditioning roll mounting shaft and the support hub to which it is mounted. The non-circular mounting shaft can be in the form of splines or standard hexagonal configuration.

BACKGROUND OF THE INVENTION

The present invention relates generally to hay harvesting machineryutilizing a conditioning mechanism and, more particularly, to a mountingstructure to permit transverse reciprocating movement of a rotatablysupported conditioning roll.

Hay harvesting machine commonly referred to as mower-conditioners orwindrowers, utilize a crop harvesting header to sever the hay crop fromthe ground and convey it rearwardly to a conditioning mechanism operableto crush or crimp the severed crop material at spaced apart intervalsalong the stem of the crop to facilitate the drainage of liquids fromthe crop material plant. Conditioning mechanisms of the type utilizing apair of counterrotating, intermeshing conditioning rolls are providedwith transversely extending flutes to effect conditioning of the severedcrop material in a manner described in greater detail in U.S. Pat. No.3,488,929 issued to J. K. Hale.

Although the individual crop material plant, which generally has a waxystem, has been broken in several places by the operation of theintermeshing flutes on the conditioning rolls, the liquids within theplant still require significant time to escape from the plant to permitsatisfactory conditions in which the dried crop material can be baledand then removed from the field. A more rapid drying of liquids from theconditioned crop material could be obtained if the waxy stem of the cropmaterial plant were split along the length thereof, providing a readymeans for the liquid to escape from the plant.

One of the problems incurred with developing a reciprocating androtating hay conditioning roll is to provide a mounting apparatuscapable of accommodating both the rotational and transverselyreciprocating linear movement of the conditioning roll. Furthercomplications in the mounting structure would be to provide a costeffective bearing surface for both rotative add linear movements.

SUMMARY OF THE INVENTION

It is an object of this invention to overcome the aforementioneddisadvantage of the prior art by providing a conditioning roll mountingapparatus capable of accommodating both rotative and transversely linearmovements for a conditioning roll.

It is another object of this invention to provide a low cost bearingstructure that will permit relative linear movement of a shaft along naxis perpendicular to the plane of rotation.

It is an advantage of this invention that the conditioning roll mountingapparatus can economically provide a means for rotatably supporting theconditioning roll while permitting axial transverse movement.

It is a feature of this invention that the conditioning roll is providedwith a non-circular mounting shaft received within a corresponding borebushing having an antifriction surface to permit axial movement relativetherebetween.

It is another feature of this invention that the bushing is in the formof a support hub pressed into the inner race of a bearing whose outerrace is fixed in the frame of the hay harvesting machine.

It is another advantage of this invention that the support hub andnon-circular shaft mounted by the support hub are mounted for rotativemovement relative to the frame of the hay harvesting machine.

It is still another feature of this invention that the support hub caneffect a rotational driving of the mounting shaft for the conditioningroll because of the non-rotative engagement therebetween.

It is a further advantage of this invention that the non-circularmounting shaft for the reciprocating conditioning roll can be in theform of a standard hexagonal configuration or in the form of axiallyextending splines.

It is yet another object of this invention to provide a conditioningroll mounting apparatus capable of accommodating both rotative andlinearly reciprocal movements on a conditioning roll, which is durablein construction, inexpensive of manufacture, carefree of maintenance,facile in assemblage, and simple and effective in use.

These and other objects, features and advantages are accomplishedaccording to the instant invention by providing a conditioning rollmounting structure is disclosed wherein the mounting shaft for theconditioning roll is permitted to be rotatably driven while permitted toreciprocate linearly transversely of the bearing apparatus. A bushing inthe form of a support hub having an antifriction surface engaged with anoncircular conditioning roll mounting shaft is pressed within the innerrace of a ball bearing whose outer race is secured to the frame of thehay harvesting machine. A drive mechanism can be attached to either thesupport hub or directly to the shaft provided that provisions are madefor accommodating the transversely reciprocating roll movement. Thestructure permits the conditioning roll to be rotatably supported withinthe frame of the hay harvesting machine, while being capable of a linearmovement between the non-circular conditioning roll mounting shaft andthe support hub to which it is mounted. The noncircular mounting shaftcan be in the form of splines or standard hexagonal configuration.

BRIEF DESCRIPTION OF THE DRAWINGS

The advantages of this invention will become apparent upon considerationof the following disclosure of the invention, especially when taken inconjunction with the accompanying drawings wherein:

FIG. 1 is a side elevational view of a hay harvesting machineincorporating the principles of the instant invention;

FIG. 2 is a top plan view of the hay harvesting machine seen in FIG. 1with the center section thereof broken away for purposes of clarity;

FIG. 3 is a partial cross-sectional view taken along lines 3--3 of FIG.2 through the conditioning mechanism to show one embodiment of thereciprocating conditioning roll structure, each conditioning roll havingthe center portion broken away to facilitate the drawing thereof, thetransverse reciprocal movement of the lower conditioning roll beingshown in phantom;

FIG. 4 is a partial cross-sectional view similar to that shown in FIG. 3to depict a second embodiment of the reciprocating conditioning rollstructure utilizing a counterweight, the transverse reciprocal movementof the lower conditioning roll being shown in phantom;

FIG. 5 is a partial cross-sectional view similar t that shown in FIG. 4to depict a third embodiment of the reciprocating conditioning rollstructure with both conditioning rolls being mounted for transversereciprocal movement as shown in phantom;

FIG. 6 is a schematic vertical crss-sectional view taken through theconditioning roll mechanism to represent a first embodiment of aconditioning roll profile; and

FIG. 7 is a view similar to that shown in FIG. 6 depicting a secondembodiment of the conditioning roll profile.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring now to the drawings and, particularly, to FIGS. 1 and 2, a hayharvesting machine, commonly referred to as a pull-typemower-conditioner, incorporating the principles of the instantinvention, can best be seen. Any left and right references are used as amatter of convenience and are determined by standing at the rear of themachine, facing the forward end, of the direction of travel.

The mower-conditioner 10 is provided with a frame 12 adapted for mobilemovement over the ground G by wheels 13 rotatably mounted thereon. Theframe 12 is provided with a pivotal draw bar 14 which extends forwardlytherefrom for connection to a prime mover, such as a tractor, in aconventional manner. The frame 12 supports a header 15 by flotationlinkage 16 for generally vertical movement relative to the ground G asis conventionally known. The header 15 includes a conventional cutterbar 17 operable to sever standing crop material from the ground G and areel 18 rotatably operable in a conventional manner to convey thesevered crop material rearwardly to the conditioning mechanism 20. Thedrive mechanism 19 is supported from the draw bar 14 and the frame 12 totransfer rotational power from the prime mover in a conventional mannerto the operable components of the mower-conditioner 10.

The conditioning mechanism 20 is shown rotatably mounted in the frame 12rearwardly of the header 15 to receive severed crop material conveyedrearwardly therefrom by the reel 18. The conditioning mechanism 20 isprovided with an upper roll 22 and a counterrotating lower roll 23positioned for intermeshing engagement therewith to define a throat 24into which the severed crop material is fed so as to pass between thecounterrotating conditioning rolls 22, 23. As depicted in Figs. 2, 6 and7, each conditioning roll is provided with a plurality ofcircumferentially spaced flutes or lugs 25 extending transversely alongthe exterior surface of the conditioning rolls 22,23. The conditioningroll profile depicted in FIG. 6, due to the arcuate configuration of theindividual intermeshing flutes 25, provide a substantially continuouscrushing of the crop material as it passes through the throat 24substantially tangential to the conditioning rolls 22, 23.Alternatively, the individual flutes 25 could have an angular shape asdepicted in FIG. 7 so as to provide crimping points at the bends of theflutes 25 to effect a conditioning of the crop material passing throughthe throat 24 along substantially regular intervals as the crop materialpasses generally tangentially to the conditioning rolls 22, 23 inaddition to the sliding conditioning action of the reciprocatingconditioning rolls described in greater detail below.

To effect an even greater conditioning of the crop material passingthrough the throat 24 between the conditioning rolls 22, 23, at leastone of the conditioning rolls 23 can be adapted for transverse linearmovement relative to the other conditioning roll 22. While the drivemechanism 19 is causing a counterrotative movement of the respectiveconditioning rolls 22, 23, through the universal joint drive couplings27, 29, an oscillating mechanism 30, shown in the form of a hydrauliccylinder 31 connected to the lower conditioning roll 23 by means of athrust bearing 32, effects the transverse reciprocating movement of thelower conditioning roll 23. The lower conditioning roll 23 is providedwith an outwardly extending axial shaft 33 which are rotatably mountedin the side sheets 34 of the frame 12 and extend outwardly therefrom inboth directions for connection with the universal joint drive coupling29 and the thrust bearing 32, respectively. The upper roll 22 isrotatably mounted in a pair of swing arms 36 operably associated with aconventional biasing mechanism (not shown) to urge the upper roll 22into intermeshing engagement with the lower roll 23; however, the swingarms 36 permit the upper roll 22 to move away from the lower roll 23within the slots 38 formed in the side sheets 34 to permit the passageof slugs or clumps of crop material through the throat 24.

Because of the transversely oriented intermeshed flutes 25 on theconditioning rolls 22, 23 and the relative sliding action created by thetransversely linearly movable mower-conditioning roll 23, it isnecessary that the drive to the conditioning rolls 22, 23 be timed tomaintain the proper intermeshed relationship between the respectiveconditioning lugs 25. The reciprocal movement of the lower conditioningroll 23 is indicated by the phantom line adjacent the right side sheet34. The transverse movement of the shaft 33 can be accommodated by thetelescopical universal joint drive coupling 29 attached to the drivemechanism 19. The timing of the stroke of the hydraulic cylinder 31 ispreferably automatically controlled either mechanically or through themeans of a microprocessor to control the flow of hydraulic fluid to thehydraulic cylinder 31.

Referring now to FIG. 4, an alternative embodiment of the conditioningmechanism 20 can be seen. Similarly to the embodiment discussed in FIG.3, only the lower conditioning roll 23 is reciprocated transversely andthe upper conditioning roll 22 is mounted for conventional verticalmovement relative to the lower conditioning roll 23. The oscillatingmechanism 40, however, is in the form of a cam mechanism 42 operablyassociated with the lower conditioning roll 23 to effect the transverselinear movement of the lower conditioning roll 23 when the conditioningroll 23 is rotated by the drive mechanism 19 as depicted associated witha hex shaft 43 protruding outwardly from either end of the lowerconditioning roll 23, as will be described in greater detail below. Thelower conditioning roll 23 is provided with a hollow core 44 in which islocated the oscillating mechanism 40 and a counterweight structure 45.The oscillating mechanism 40 also includes a second cam mechanism 47operable to effect a transversely linear reciprocating movement of thecounterweight 45 in opposition to the transverse movement of the lowerconditioning roll 23 to provide a counterbalance and improve stabilityfor the mower-conditioner 10.

Each of the cam mechanisms 42, 47 depicted in FIG. 4 includes a camtrack 49, 56 inclined relative to the transversely extending axis of thelower conditioning roll 23. Each cam mechanism 42, 47 is also providedwith a cam roller 51, 58 which is secured on a support arm 52, 59attached rigidly to the respective side sheet 34 the frame 12 andengaged with the corresponding cam track 49, 56. The first cam mechanism42 is shown with the cam track 49 affixed to the internal circumferenceof the core 44 of the lower roll 23. Since the cam roller 51 is fixedrelative to the right side sheet 34 and since the entire lower roll 23is mounted for movement transversely relative to the side sheet 34, theengagement between the cam roller 51 within the cam track 49 causes thetransverse linear movement Of the lower conditioning roll 23 when thelower conditioning roll 23 is rotated by the drive mechanism 19. Thelength of the stroke of reciprocating movement of the lower conditioningroll 23 is determined by the angle of inclination of the cam track 49relative to the axis of the conditioning roll.

The counterweight mechanism 45 is slidably mounted on the hex shaft 43to be rotatable therewith while permissive of transverse movementrelative to the lower conditioning roll 23. The counterweight mechanism45 is provided with a cam track 56 built-in. The angle of inclination ofthe cam track 56 is equal to, but opposite of, the angle of inclinationof the cam track 49 of the first cam mechanism 42. Similar to the firstcam mechanism 2, the second cam mechanism 47 is provided with a camroller 58 mounted on a support arm 59 rigidly secured to the left sidesheet 34 so that the distance between the cam roller 58 and the leftside sheet 34 is fixed. When the counterweight mechanism 45 is rotatedwith the hex shaft 43 and the lower conditioning roll 23, the engagementbetween the cam roller 58 and the cam track 56 effect a linearlytransverse movement of the counterweight mechanism 45 along the hexshaft 43 in opposition to the transverse movement of the lowerconditioning roll 23. Since the mass of the counterweight mechanism 45is substantially equal to the mass of the lower conditioning roll 23,the oppositely moving masses of the counterweight 45 and the lowerconditioning roll 23 counterbalance. One skilled in the art will readilyrealize that other cam mechanism configurations or wobble devices wouldbe equally applicable and equally effective to cause an opposingtransverse movement of the counterweight 45 and lower conditioning roll23.

Continuing with reference to FIG. 4, the bearing mechanism for rotatablysupporting the lower conditioning roll 23 for transverse reciprocalmovement can best be seen. Rotational power to the lower conditioningroll 23 could be provided by a chain drive mechanism which would includea sprocket 61 cooperable therewith. A hex bore bushing support hub 63 ismounted on the hex shaft 43 to be rotatable therewith. The hex borebushing 63 is pressed into the inner race 66 of a ball bearing 65 whoseouter race is secured to the side sheet 34 of the frame 12. As a result,the hex bore bushing 63 and hex shaft 43 are rotatably supported withinthe side sheet 34. The hex bore bushing 63 has an antifriction internalsurface and provides a bushing area for the transverse linearreciprocating movement of the hex shaft 43. By incorporating the chainsprocket 61 into the body of the hex bore bushing 63, rotational driveimparted to the chain sprocket 61 by a drive chain (no shown) will betransferred directly to the hex shaft 43 to effect a rotative movementof the lower conditioning roll 23. Accordingly, a low cost bearingsurface capable of accommodating both rotational and linearlyreciprocating movement is provided.

Referring now to FIG. 5, a third embodiment of the reciprocatingconditioning roll mechanism 20 can best be seen. Contrary to theembodiments described above relative to FIGS. 3 and 4, both the upperconditioning roll 22 and the lower conditioning roll 23 are reciprocatedtransversely relative to one another. The oscillating mechanism 70 isshown in the form of a cam mechanism 72 operatively associated with theupper conditioning roll 22 and a second cam mechanism 73 operativelyassociated with the lower conditioner roll 23. As noted above withrespect to the oscillating mechanism 40, the first and second cammechanisms 72, 73 include an inclined cam track 76 and an associated camroller 77 mounted on support arm 78 affixed to the respective sidesheets 34 to provide reciprocal movement to the respective conditioningrolls 22, 23.

Because both the upper conditioning roll 22 and the lower conditioningroll 23 are being reciprocated equally, the angle of inclination of thecam track 76 is equal in both the cam mechanism 72, 73, but is only halfof the angle of inclination required in the embodiment depicted in FIG.4 to effect an identical amount of relative reciprocal movement. Asdescribed above with respect to the embodiment shown in FIG. 4, the cammechanisms 72, 73 are housed within the core 74 of the conditioningrolls 22, 23. Because of the counterrotation of the respective rolls 22,23, the angle of inclination of the cam track 76 on the cam mechanism72, 73 is essentially identical but effect opposing reciprocatingmovement of the respective conditioning rolls 22, 23.

It would be preferable to place the cam track 76 on the cam mechanism 72slightly out of phase with the cam track 76 of the cam mechanism 73 sothat the reciprocal movement of the respective conditioning rolls 22, 23is not exactly opposing, although nearly so. This out of phase alignmentof the respective cam mechanism 72, 73 would result in a continuousrelative reciprocal movement of the conditioning mechanism 20, ascompared to the dead spot encountered when the conditioning rolls 22,23would reach the limit of reciprocation simultaneously if they were inphase.

FIG. 5 also depicts an alternative bearing arrangement for accommodatingboth rotational and reciprocal movements of the conditioning rolls 22,23. Compared with the embodiment described above relative to FIG. 4, theshafts 81 corresponding to the respective conditioning rolls 22, 23 aresplined and are slidably received within the splined corresponding boreof a bushing or support hub 83 rotatably mounted within the inner race86 of a ball bearing 85 whose outer race 87 is secured to the applicableside sheet 34 of the frame 12. As a result, the bushing 83 is rotatablewith the splined shaft 81 but, because of an antifriction internalsurface engaged with the shafts 81 as described above relative to thesupport hub 63, also permits relative linear movement therebetween.Rotational power can be provided to the respective shafts 81 from thedrive mechanism 19 coupled thereto with telescopic universal joint drivecouplings 89.

Because of the need to provide generally vertical movement of the upperconditioning roll 22 relative to the lower conditioning roll 23, asdescribed relative to the embodiment shown in FIG. 3 above, the bearings85 and associated bushings 83 for the upper roll 22 must be carried bythe respective swing arms 36 to facilitate the vertical movement whilethe upper conditioning roll 22 is being transversely reciprocated. Sincethe drive 19 is timed to the respective conditioning rolls 22, 23, thereengagement of the upper conditioning roll 22 with the lowerconditioning roll 23 will be accomplished in proper intermeshingrelationship.

It will be understood that changes in the details, materials, steps andarrangements of parts which have been described and illustrated toexplain the nature of the invention will occur to and may be made bythose skilled in the art upon a reading of this disclosure within theprinciples and scope of the invention. The foregoing descriptionillustrates the preferred embodiment of the invention; however, conceptsas based upon the description may be employed in other embodimentswithout departing from the scope of the invention. Accordingly, thefollowing claims are intended to protect the invention broadly as wellas in the specific form shown.

Having thus described the invention, what is claimed is:
 1. In aharvesting machine having a mobile frame adapted for movement over afield to harvest crop material from the field; a crop harvesting headersupported from said frame to collect crop material from the field andconvey the collected crop material for further harvesting action; aconditioning mechanism positioned in flow communication with said cropharvesting header to receive said collect crop material therefrom andeffect a conditioning thereof, said conditioning mechanism including apair of counter-rotating conditioning rolls operable to condition cropmaterial passing therebetween; and drive means operatively connected tosaid crop harvesting header and said conditioning mechanism tooperatively power the operation thereof, the improvementcomprising:bearing means for rotatably supporting at least one of saidconditioning rolls, said bearing means being supported from said frameand being adapted to permit a reciprocating linear motion of said atleast one conditioning roll; and oscillating means operatively connectedto said at least one conditioning roll to effect a reciprocatingtransverse linear movement thereof.
 2. The harvesting machine of claim 1wherein said bearing means includes an outer race fixedly supported bysaid frame; an inner race rotatably supported from said outer race androtatable relative thereto; and a support hub fixed to said inner raceto be rotatable therewith, said support hub mounting said at least oneconditioner roll and permitting linear movement of said at least oneconditioning roll relative thereto.
 3. The harvesting machine of claim 2wherein said at least one conditioning roll has an axially alignedshaft, said support hub receiving said shaft to permit linear movementof said shaft relative thereto.
 4. The harvesting machine of claim 3wherein said shaft has a configuration preventing rotative movementthereof relative to said support hub.
 5. The harvesting machine of claim4 wherein said shaft has a hexagonal cross-sectional configurationcorresponding to a hexagonal bore though said support hub.
 6. Theharvesting machine of claim 4 wherein said shaft is provided withsplines corresponding to a ribbed bore through said support hub.
 7. Theharvesting machine of claim 4 wherein said support hub is pressed intosaid inner race so as to be rotatable therewith.
 8. The harvestingmachine of claim 7 wherein said support hub has an anti-friction borereceiving said shaft so that said shaft is linearly movable relativethereto while being rotatable therewith.
 9. The harvesting machine ofclaim 8 wherein said support hub has a drive sprocket secured theretoand operatively associated with said drive means to effect rotation ofsaid at least one conditioning roll.
 10. A mechanism for mounting aconditioning roll in a crop harvesting machine to permit a rotativemovement of said conditioning roll and a linear reciprocating movementof said conditioning roll comprising:a bearing having a fixed outer raceand a rotatable inner race to rotatably support said conditioner roll;and a support hub fixed to said inner race to be rotatable therewith,said support hub having a bore therethrough to receive a mounting shaftconnected to said conditioning roll, said support hub having ananti-friction surface in said bore to permit a linear movement of saidmounting shaft relative to said support hub, said mounting shaft beingoperatively connected to means for linearly reciprocating saidconditioning roll so that said mounting shaft is linearly movablerelative to said support hub.
 11. The mounting mechanism of claim 10wherein said mounting shaft has a configuration corresponding to saidsupport hub bore such that said mounting shaft is rotatable with saidsupport hub and said inner race.
 12. The mounting mechanism of claim 11wherein said mounting shaft has a hexagonal cross-sectionalconfiguration corresponding to a hexagonally shaped support hub bore.13. The mounting mechanism of claim 11 wherein said mounting shaft issplined to correspond to a ribbed support hub bore so that said mountingshaft is rotatable with said support hub.
 14. The mounting mechanism ofclaim 11 wherein said support hub is pressed into inner race.
 15. Themounting mechanism of claim 14 wherein said support hub has a driveapparatus affixed thereto for effecting a rotational driving of saidconditioning roll.